Variable flow valve having metered flow orifice

ABSTRACT

A variable flow valve assembly is disclosed, and includes a main body, a piston, a position sensor, a controller, a solenoid, and a cover. The main body defines a chamber, an inlet port, an outlet port, and a wall located between the inlet port and the outlet port. The wall defines a metering orifice for selectively allowing a medium to flow from the inlet port to the outlet port. The chamber of the main body includes a pressurized chamber. The piston is moveable within the chamber of the main body in a plurality of partially open positions to vary the amount of medium flowing through the modulation orifice. The piston separates the pressurized chamber from the inlet port. The position sensor determines the position of the piston within the chamber of the main body, and the controller is in signal communication with the position sensor.

RELATED APPLICATIONS

This application is a continuation application of U.S. application Ser.No. 14/269,286, filed on May 5, 2014.

TECHNICAL FIELD

The present invention relates generally to a variable flow valve, wherethe valve includes a metering orifice for modulating the amount of flow.

BACKGROUND

Internal combustion engines may be used in a variety of applicationssuch as, for example, passenger and industrial vehicles, marine,stationary and aerospace applications. There are generally two dominantignition cycles, which are commonly referred to as gas and dieselcycles, or more formally as spark ignited (SI) and compression ignition(CI) cycles, respectively.

Exhaust-driven turbochargers may be used to improve the power output andoverall efficiency of an internal combustion engine. Specifically,exhaust gas energy may be used to drive a turbine. The turbochargerincludes a compressor and a turbine, where the compressor is mounted ona shaft of the turbocharger, opposite the turbine. The turbine convertsengine exhaust gas into mechanical energy, which is used to drive thecompressor. The compressor draws in and compresses air. The compressedair is then directed to an intake manifold of the internal combustionengine.

A relief valve, such as a compressor discharge valve or a blow-offvalve, may be mounted on an intake pipe located downstream of theturbocharger before a throttle. Specifically, a compressor dischargevalve may be used to vent compressed air back into an inlet of thecompressor. A blow-off valve is similar to a compressor recirculationvalve, but vents to the atmosphere rather than back to the inlet of thecompressor. The relief valve may be used to alleviate a sudden surge orspike in pressure that may occur when the throttle closes (i.e., when anoperator suddenly lifts his or her foot off of the gas pedal and thethrottle closes). Some types of relief valves currently available mayonly be completely opened or shut. In other words, some relief valves donot provide active control of the position of the valve.

SUMMARY

The disclosed variable flow valve assembly includes a modulation orificethat varies the amount of medium, such as air or fluid, that flowsthrough the relief valve. Specifically, in one aspect, a variable flowvalve assembly is disclosed and includes a main body, a piston, aposition sensor, a controller, a solenoid, and a cover. The main bodydefines a chamber, an inlet port, an outlet port, and a wall locatedbetween the inlet port and the outlet port. The wall defines a meteringorifice for selectively allowing a medium to flow from the inlet port tothe outlet port. The chamber of the main body includes a pressurizedchamber. The piston is moveable within the chamber of the main body in aplurality of partially open positions to vary the amount of mediumflowing through the modulation orifice. The piston separates thepressurized chamber from the inlet port. The position sensor determinesthe position of the piston within the chamber of the main body, and thecontroller is in signal communication with the position sensor. Thesolenoid is in signal communication with the controller. The cover islocated within the chamber of the main body, and provides sealingbetween the pressurized chamber and the atmosphere.

In another aspect, a system for controlling an exhaust driventurbocharging system is disclosed. The system includes a turbochargerhaving a compressor inlet in fluid communication with a variable flowvalve assembly and an intake manifold of an engine. The variable flowvalve assembly includes a main body and a piston. The main body definesa chamber, an inlet port, an outlet port, and a wall located between theinlet port and the outlet port. The wall defines a metering orifice forselectively allowing a medium to flow from the inlet port to the outletport. The chamber of the main body includes a pressurized chamber. Thepiston is moveable within the chamber of the main body in a plurality ofpartially open positions to vary the amount of medium flowing throughthe modulation orifice. The piston separates the pressurized chamberfrom the inlet port. The system also includes a position sensor, acontroller, a solenoid, and a cover. The position sensor determines theposition of the piston within the chamber of the main body. Thecontroller is in signal communication with the position sensor. Theposition of the piston within the chamber is determined by thecontroller. The metering orifice is partially opened in order tocommunicate air into the intake manifold of the engine. The solenoid isin signal communication with the controller. The solenoid applies apredetermined amount of vacuum to the pressurized chamber. Thepredetermined amount of vacuum causes the piston to move into one of theplurality of open positions. The cover provides sealing between thepressurized chamber and the atmosphere.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a diagram including flow paths and flow directions of oneembodiment of an internal combustion engine turbo system that includes arelief valve.

FIG. 2 is a perspective, partially transparent view of one embodiment ofthe relief valve in a closed position.

FIG. 3 is a cross-sectional view of the relief valve of FIG. 2 in theclosed position.

FIG. 4 is a cross-sectional view of the relief valve of FIG. 2 in anopen position.

FIG. 5 is a cross-sectional view of the relief valve of FIG. 2 fluidlyconnected to a solenoid in the closed position.

FIG. 6A is a front view of the relief valve in the closed position.

FIG. 6B is a front view of the relief valve in a partially openposition.

FIG. 6C is a front view of the relief valve in the open position.

DETAILED DESCRIPTION

The following detailed description will illustrate the generalprinciples of the invention, examples of which are additionallyillustrated in the accompanying drawings. In the drawings, likereference numbers indicate identical or functionally similar elements.

Referring now to FIG. 1, an exemplary schematic diagram of a turbosystem 10 for an internal combustion engine 12 is illustrated. The turbosystem 10 may include an exhaust-driven turbo charger (“EDT”) 20 havinga turbine section 22 and compressor section 24, a turbine bypass valveor wastegate 26, and a relief valve 30. An exhaust housing 18 of the EDT20 contains a turbine wheel 32. A turbine wheel 32 harnesses andconverts exhaust energy into mechanical work through a common shaft 34to turn a compressor wheel 35. The compressor wheel 35 ingests,compresses and feeds air at elevated operating pressures into an intakemanifold 36 of the internal combustion engine 12.

The wastegate 26 is a control valve used to meter an exhaust volume 37exiting an exhaust manifold 40 of the internal combustion engine 12, andcontrols the amount of energy available to power the turbine wheel 32.The wastegate 26 works by opening a valve (not shown) connected to abypass pipe 42. Opening the valve of the wastegate 26 allows for exhaustto flow away from the turbine wheel 32. Thus, the wastegate 26 may havedirect control over the speed of the EDT 20 and the resultant operatingpressure of the intake manifold 36 of the internal combustion engine 12.The wastegate 26 may have any number of embodiments, including theembodiments disclosed in applicant's U.S. Pat. No. 8,469,333, which isincorporated by reference herein in its entirety.

Operating pressures exist in an EDT compressor inlet 50, the intakemanifold 36 of the internal combustion engine 12 and an intake manifoldpipe 52, the exhaust manifold 40 of the internal combustion engine 12and an intake manifold pipe 54, an exhaust inlet 58 of the EDT 20, andan exhaust outlet 59 of the EDT 20. Specifically, the EDT compressorinlet 50 may be defined as the passageway from an air intake system 60to an inlet 64 of the compressor section 24. The intake manifold 36 ofthe internal combustion engine 12 may be defined as the passage betweenan EDT compressor discharge 66 and one or more intake valves 68 of theinternal combustion engine 12. The exhaust manifold 40 of the internalcombustion engine 12 may be defined as the passage between one or moreexhaust valves 70 and the exhaust inlet 58 of the EDT. The exhaust maybe any passageway located after the exhaust outlet 59 of the EDT 20. Inorder to achieve effective exhaust gas recirculation (EGR), thepressures in an exhaust manifold should be significantly higher than thepressures found in an intake manifold in order for exhaust gas to flowin the correct direction. Smaller EDT exhaust profiles produce higherdesired exhaust manifold pressures, but at the expense of lowerefficiencies. Thus, those skilled in the art will appreciate that a finebalance exists between achieving efficiency of the internal combustionengine 12 and EGR effectiveness.

The relief valve 30 may be a regulating valve located in the intakemanifold pipe 52 between the compressor discharge 66 of the compressorsection 24 of the EDT 20 and the intake manifold 36 of the internalcombustion engine 12. In the embodiment as shown in FIG. 1, the reliefvalve 30 is a compressor recirculation valve that is fluidly connectedto and vents compressed air back into the EDT compressor inlet 50.However, it should be noted that in another embodiment, the turbo system10 may utilize a blow-off valve as well. A blow-off valve is similar toa compressor recirculation valve, but vents to the atmosphere ratherthan back to the compressor inlet of an EDT. A solenoid 38 may beconnected to the relief valve 30. In one embodiment, the solenoid 38 maybe used to apply vacuum to and actuate the relief valve 30, which isdescribed in greater detail below.

In the exemplary embodiment as shown in FIG. 1, the relief valve 30 maybe used with a spark ignited internal combustion engine 12 and athrottle plate 80. At any given operating range of the internalcombustion engine 12, the shaft 34 of the EDT 20 may be spinning up to200,000 revolutions per minute (RPM). A sudden closing of the throttle80 does not immediately decelerate the RPM of the EDT 20. Therefore,this closing creates a sudden increase in pressure in the passagesbetween the closed throttle 80 and EDT compressor section 24 (e.g., theintake manifold pipe 52). The relief valve 30 may be used to relieve orbypass the pressure created by the sudden closing of the throttle 80.

When the relief valve 30 is opened the EDT 20 may spin freely, therebyconserving the inertia of the EDT 20. If the relief valve 30 wasomitted, the EDT 20 would stall or stop once the throttle 80 is closed.This stalling or stopping may adversely affect EDT life and throttleresponse. Those skilled in the art will appreciate that the EDT 20should be spinning and ready to produce boost as soon as the throttleplate 80 is opened. The relief valve 30 may decrease turbo lag byallowing the EDT 20 to spin up to speed (i.e., spool up) withoutcompressor load, as there is no back pressure present once the reliefvalve 30 is opened. A variable relief valve, which is described ingreater detail below, may be especially beneficial by allowing just theamount of bypass to be ready for immediate boost to substantiallyprevent compressor surge. Compressor surge may be defined as when theair pressure after the compressor wheel 35 is actually higher than whatthe compressor wheel 35 is capable of maintaining. This condition causesthe airflow in the compressor wheel 35 to back up, build pressure, orstall. Thus, compressor surge is noisy, affects EDT life, and may reducethe performance of the turbo system 10.

The relief valve 30 may be employed in any EDT enabled internalcombustion engine, including a diesel engine. Although a turbo system 10is disclosed, those skilled in the art will readily appreciate that therelief valve 30 may be used in any application where the flow of amedium such as fluid or gas may be modulated or varied. In other words,the relief valve 30 may include a plurality of partially openedpositions to vary the amount of exhaust gas to the intake manifold 36 ofthe internal combustion engine 12 (FIG. 1).

Referring to FIGS. 2-3, the relief valve 30 may include a valve body 100that defines an inlet port 102, an outlet port 104, and a pressurizedchamber 106. In the exemplary embodiment as shown in FIGS. 2-3, thelower port is the inlet port 102, and the port located on the right handside of the valve body 100 is the outlet port 106. However, it is to beunderstood that the direction of flow 108 may be reversed, and the port102 may be used as an outlet port, and the port 104 may be used as aninlet port. The valve 30 may also include a snap ring 110, a cover 112,a biasing element 114, a piston 120, a vent fitting 122, a vent fitting124, and a magnet 126. The snap ring 110 may define one or more eyelets130 (FIG. 2). The snap ring 110 may be seated within an annular recess132 located at a first end 134 of the valve body 100.

In the exemplary embodiment as shown in FIGS. 2-3, the valve body 100may define a generally cylindrical chamber 136 extending between thefirst end 134 and a second end 138. The piston 120 may be sized totranslate in a linear direction within the chamber 136 of the valve body100. The piston 120 may also separate the inlet port 102 from thepressurized chamber 106. FIGS. 2-3 illustrate the valve 30 in a closedposition, and FIGS. 4 and 6C illustrate the valve 30 in an openposition. Specifically, the piston 120 may translate or move up and downincrementally within the cylindrical chamber 136 of the valve body 100.As best seen in FIG. 3, a metering or modulation orifice 142 may bedefined by a generally cylindrical wall 140 that defines a portion ofthe chamber 136. The wall 140 may include a first side 144 and a secondside 146. The first side 144 of the wall 140 may define a portion of theoutlet port 104, and the second side 146 of the wall 140 may define aportion of the chamber 136.

The modulation orifice 142 may be used to selectively allow for amedium, such as fluid or gas, to flow from the inlet port 102 to theoutlet port 104. The modulation orifice 142 may also be used to vary ormodulate the amount of medium that passes from the inlet port 102 to theoutlet port 104. Specifically, when the valve 30 is in the closedposition (FIGS. 2-3 and 6A), the piston 120 may generally block orprevent a medium from flowing from the inlet port 102 to the outlet port104. The piston 120 may be actuated into a plurality of partially openedpositions (one of which is shown in FIG. 6B) in response to signalsgenerated by a position sensor 150, which is described in greater detailbelow. The piston 120 is moveable within the chamber 136 of the valve100 in a plurality of partially opened positions, which in turn variesthe amount of medium that may flow through the modulation orifice 142.When the relief valve 30 is in the completely open position (FIG. 4), amedium may flow through the modulation orifice 142 without anysubstantial obstruction or blockage by the piston 120.

As best seen in FIGS. 3-4, the piston 120 may include an upper surface148 and a lower surface 149. Two sealing members 168 and 169 may beseated within the cylindrical chamber 136 of the valve body 100.Specifically, if the relief valve 30 is in the closed position, thesealing member 168 may be aligned with and provide sealing between thepressurized chamber 106 of the valve body 100, the modulation orifice142, and the piston 120. Likewise, the sealing member 169 may be alignedwith and provide sealing between the inlet port 102 of the valve body100, the modulation orifice 142, and the piston 120. The sealing members168, 169 may be any type of seal for reciprocating components such as anO-ring.

In the exemplary embodiment as shown, the modulation orifice 142includes a generally inverted triangular profile. Thus, as the piston120 moves upwardly from the closed position (FIGS. 2-3) and into theopen position (FIG. 4), the amount of flow passing through themodulation orifice 142 increases exponentially. In other words, as thelower surface 149 of the piston 120 is moved into the fully openposition, the amount of flow through the modulation orifice 142 mayincrease at a faster rate. Although an inverted triangle is illustrated,those skilled in the art will readily appreciate that the modulationorifice 142 may take on a variety of different shapes and configurationsin order to control the amount of flow. The shape of the modulationorifice 142 may depend upon a number of variables such as, but notlimited to, noise (i.e., to control whistling through the valve 30) andthe distance the piston 120 may travel within the cylindrical chamber136 of the valve body 100. For example, in an alternative embodiment,the modulation orifice 142 may include a slotted or squareconfiguration.

Referring to FIG. 3, the cover 112 may be located within the pressurizedchamber 106 of the valve body 100. The cover 112 includes a body 152having an open end 154 and a closed end 156. A lip or rim 158 may belocated at the open end 154 of the body 152. The valve body 100 maydefine a shelf 160. The rim 158 of the cover 112 may be seated againstthe shelf 160 of the valve body 100. A sealing element 162 such as, forexample, an O-ring may be interposed between a side surface 164 of therim 158 and a side surface 166 of the valve body 100. The cover 112provides sealing between the pressurized chamber 106 of the valve body100 and the atmosphere.

The body 152 of the cover 112 also defines a recess 170. A controller172 and the position sensor 150 may be located within the recess 170 ofthe cover 112, where the controller 172 is in signal communication withthe position sensor 150. The controller 172 may refer to an applicationspecific integrated circuit (ASIC), an electronic circuit, a processor(shared, dedicated, or group) and memory that executes one or moresoftware or firmware programs, a combinational logic circuit, or othersuitable components that provide the described functionality.

The position sensor 150 may be any device that permits positionmeasurement. In one embodiment, position sensor 150 is a relativeposition sensor (a displacement sensor) based on movement of the piston120 within the cylindrical chamber 136 of the valve body 100. Theposition sensor 150 may be a capacitive transducer, an eddy-currentsensor, a grating sensor, a Hall effect sensor, an inductive non-contactposition sensor, a laser Doppler Vibrometer (optical), a linear variabledifferential transformer (LVDT), a multi-axis displacement transducer, aphotodiode array, a piezo-electric transducer (piezo-electric), apotentiometer, a proximity sensor (optical), a seismic displacementpick-up, a string potentiometer (also known as string pot., stringencoder, cable position transducer), or a combination thereof

In the embodiment illustrated, the position sensor 150 is a Hall effectsensor comprising a chip/Hall effect position sensor 174 that sensorsthe displacement of the magnet 126. The magnet 126 may be connected tothe piston 120 for translation therewith. Specifically, the magnet 126may be mounted to or placed within the piston 120. In FIGS. 3 and 4, themagnet 126 is housed within a bracket 178 formed by a piston body 180.The bracket 178 suspends the magnet 126 within the piston 120.

The chip/Hall effect position sensor 174 may be positioned within thevalve body 100 in sufficient proximity to sense the movement of themagnet 126 located within the piston 120, and determine the specificposition of the piston 120 within the chamber 136 of the valve body 100.In the embodiment as shown in FIGS. 3 and 4, the chip/Hall effectposition sensor 174 is oriented horizontally in a position above themagnet 126 (i.e., axial relative to the magnet 126). In anotherembodiment, the chip/Hall effect position sensor 174 may be orientedvertically in a position radially outward away from the magnet 126.

The biasing element 114 may include a first end 180 and a second end182. The first end 180 of the biasing element 114 may be seated againstthe rim 158 of the cover 112, and the second end 182 of the biasingelement 114 may be seated against the upper surface 148 of the piston120. The biasing element 114 may be used to exert an axial force againstthe upper surface 148 of the piston 120. In the non-limiting embodimentas shown, the biasing element 114 is a coil spring, however thoseskilled in the art will appreciate that any type of biasing element forexerting an axial force against the piston 120 may be used as well.

FIG. 5 is an illustration of the relief valve 30 and the solenoid 38.The solenoid 38 may be used to create a pressure differential within therelief valve 30, thereby causing the piston 120 to travel within thechamber 136 of the valve body 100. Although a solenoid is illustrated,those skilled in the art will appreciate that other devices may be usedas well to create a pressure differential within the relief valve 30such as, for example, a pump for moving fluid or gas in either apositive or a negative direction.

The controller 172 may be in signal communication with the solenoid 38in order to turn on the solenoid 38 and to move an armature (notillustrated). Specifically, the controller 172 may control the solenoid38 based on the current position of the piston 120 within the chamber136. The movement of the armature of the solenoid 38 may create apressure differential between the inlet port 102 and the pressurizedchamber 106 of the valve body 100. The piston 120 may translate or movewithin the chamber 136 of the valve body 100 based on a pressuredifferential between the inlet port 102 and the pressurized chamber 106,which is described in greater detail below.

In the embodiment as shown in FIG. 5, the solenoid 38 may include afirst vent port 190, a second vent port 194, and a vacuum port 196. Thefirst vent port 190 of the solenoid 38 may be fluidly connected to thevent fitting 122 of the valve 30, and the second vent port 194 may befluidly connected to the vent fitting 124 of the valve 30. In oneembodiment, the first vent port 190 and the second vent port 194 may befluidly connected to the relief valve 30 using a connection hose (notillustrated). FIG. 5 illustrates the valve 30 in the closed position,where the controller 172 may control the armature of the solenoid 38(not illustrated) in order to open the first vent port 190 and close thevacuum port 196 to communicate pressure between the first vent port 190and the second vent port 194. Thus, the pressure of the inlet port 102is about equal to or balanced with the pressurized chamber 106 of thevalve body 100. The axial force exerted by the biasing element 114against the upper surface 148 of the piston 120 retains the piston 120in place in the closed position within the chamber 136 of the valve body100.

The controller 172 may control the solenoid 38 in order to create apressure differential between the inlet port 102 and the pressurizedchamber 106 of the valve body 100. Specifically, the controller 172 maycontrol the armature of the solenoid 38 (not illustrated) in order toclose the first vent port 190 and apply vacuum to the second vent port194. Thus, the pressure of the inlet port 102 is no longer equal to thepressure located within the pressurized chamber 106 of the valve body100. As a result, the piston 120 overcomes the axial force exerted bythe biasing element 114, and the piston 120 may translate in an upwarddirection, and into the open position seen in FIG. 4. In one embodiment,the amount of vacuum applied to the second vent port 194 may be variedin order to control the position of the piston 120 within the chamber136 of the valve body 100. In other words, the piston 120 may bepositioned in one of the partially opened positions based on apredetermined amount of vacuum applied to the second vent port 194. Inan alternative embodiment, the position of the piston 120 may becontrolled using pulse width modulation (PWM) control. Specifically, thesolenoid 38 may be modulated off and on using PWM control in order toposition the piston 120 in one of the partially opened positions withinthe chamber 136 of the valve body 100.

Referring generally to the figures, the disclosed relief valve 30includes a modulation orifice, which is used to vary the amount ofmedium that flows through the relief valve. Thus, referring specificallyto FIG. 1, the relief valve 30 enables the control of an operatingpressure of the exhaust manifold 40 on command. In particular, bypartially opening the disclosed valve 30, the operating pressures in theexhaust manifold 40 may be controlled. Some types of compressorrecirculation valves and blow-off valves currently available only have afully open or a fully closed position. In contrast, the disclosed valve30 may be opened into a plurality of positions, thereby allowing controlof the operating pressure in the exhaust manifold 40 on command. This inturn will allow for more precise control of turbo speed. Moreover, turboresponse time and turbo lag may be reduced. Finally, the disclosedrelief valve 30 may also improve fuel economy as well as drivability ofa vehicle.

The embodiments of this invention shown in the drawings and describedabove are exemplary of numerous embodiments that may be made within thescope of the appended claims. It is contemplated that numerous otherconfigurations of the tensioner may be created taking advantage of thedisclosed approach. In short, it is the applicant's intention that thescope of the patent issuing herefrom will be limited only by the scopeof the appended claims.

What is claimed is:
 1. A variable flow valve assembly, comprising: amain body defining a chamber, an inlet port, an outlet port, and a walllocated between the inlet port and the outlet port, the wall defining ametering orifice for selectively allowing a medium to flow from theinlet port to the outlet port, wherein the chamber of the main bodyincludes a pressurized chamber; a piston moveable within the chamber ofthe main body in a plurality of partially open positions to vary theamount of medium flowing through the modulation orifice, wherein thepiston separates the pressurized chamber from the inlet port; a positionsensor for determining the position of the piston within the chamber ofthe main body; a controller that is in signal communication with theposition sensor; a solenoid in signal communication with the controller;and a cover located within the chamber of the main body, the coverproviding sealing between the pressurized chamber and the atmosphere. 2.The variable flow valve assembly of claim 1, wherein the position sensoris a Hall effect sensor comprising a sensor chip that sensors thedisplacement of a magnet seated within the piston.
 3. The variable flowvalve assembly of claim 1, wherein the solenoid applies a predeterminedamount of vacuum to the pressurized chamber, and wherein thepredetermined amount of vacuum causes the piston to move into one of theplurality of open positions.
 4. The variable flow valve assembly ofclaim 1, wherein the solenoid is modulated using pulse width modulation(PWM) control in order to position the piston in one of the partiallyopened positions within the chamber of the main body.
 5. The variableflow valve assembly of claim 1, further comprising a biasing elementthat includes a first end and a second end, wherein the first end of thebiasing element is seated against the cover, and the second end of thebiasing element is seated against an upper surface of the piston.
 6. Thevariable flow valve assembly of claim 1, wherein the metering orificeincludes a triangular, a slotted, or a rectangular configuration.
 7. Thevariable flow valve assembly of claim 1, wherein the variable flow valveis one of a compressor recirculation valve and a blow-off valve.
 8. Thevariable flow valve assembly of claim 1, wherein the metering orificedefines a predefined shape.
 9. The variable flow valve assembly of claim8, wherein the piston is sized to translate a predefined distance withinthe chamber of the main body, and wherein the predefined shape of themetering orifice is based at least in part by the predefined distancethe piston travels within the chamber so as to partially cover themetering orifice with the piston in the plurality of open positions. 10.The variable flow valve assembly of claim 8, wherein the predefinedshape of the metering orifice includes a generally inverted triangularprofile.
 11. The variable flow valve assembly of claim 10, wherein asthe piston moves upwardly from a fully closed position and into one ofthe plurality of open positions, the medium flowing through themodulation orifice increases exponentially.
 12. A system for controllingan exhaust driven turbocharging system, comprising: a turbochargerhaving a compressor inlet in fluid communication with a variable flowvalve assembly and an intake manifold of an engine, the variable flowvalve assembly comprising: a main body defining a chamber, an inletport, an outlet port, and a wall located between the inlet port and theoutlet port, the wall defining a metering orifice for selectivelyallowing a medium to flow from the inlet port to the outlet port,wherein the chamber of the main body includes a pressurized chamber; anda piston moveable within the chamber of the main body in a plurality ofpartially open positions to vary the amount of medium flowing throughthe modulation orifice, wherein the piston separates the pressurizedchamber from the inlet port; a position sensor for determining theposition of the piston within the chamber of the main body; a controllerthat is in signal communication with the position sensor, wherein theposition of the piston within the chamber is determined by thecontroller, and wherein the metering orifice is partially opened inorder to communicate air into the intake manifold of the engine; asolenoid in signal communication with the controller, wherein thesolenoid applies a predetermined amount of vacuum to the pressurizedchamber, and wherein the predetermined amount of vacuum causes thepiston to move into one of the plurality of open positions; and a coverproviding sealing between the pressurized chamber and the atmosphere.13. The system of claim 12, further comprising a biasing element thatincludes a first end and a second end, wherein the first end of thebiasing element is seated against the cover, and the second end of thebiasing element is seated against an upper surface of the piston. 14.The system of claim 12, wherein the metering orifice includes atriangular, a slotted, or a rectangular configuration.
 15. The system ofclaim 12, wherein the variable flow valve assembly is a compressorrecirculation valve that is fluidly connected to and vents compressedair back into the compressor inlet.
 16. The system of claim 12, whereinthe variable flow valve is one of a compressor recirculation valve and ablow-off valve.
 17. The system of claim 12, wherein the metering orificedefines a predefined shape.
 18. The system of claim 17, wherein thepiston is sized to translate a predefined distance within the chamber ofthe main body, and wherein the predefined shape of the metering orificeis based at least in part by the predefined distance the piston travelswithin the chamber so as to partially cover the metering orifice withthe piston in the plurality of open positions.
 19. The system of claim17, wherein the predefined shape of the metering orifice includes agenerally inverted triangular profile.
 20. The system of claim 19,wherein as the piston moves upwardly from a fully closed position andinto one of the plurality of open positions, the medium flowing throughthe modulation orifice increases exponentially.